what type of mate would you use to align a rod in a hole?

Design with SolidWorks

Kuang-Hua Chang , in Design Theory and Methods Using CAD/CAE, 2015

S5.3.i.1 Motility model and simulation

Start SolidWorks and open up "Engine.sldasm" under the folder "Lesson S5.3 Unmarried-Piston Engine." Yous should see the engine assembly, as shown in Figure S5.22a. There are 21 associates mates defined to create the move model (see Figure S5.22a). I of them, Angle1, which is created to define the initial rotation angle of the spinner, is suppressed to provide the free caste of freedom. Y'all may want to browse some of the associates mates to gain a ameliorate agreement of the assembly and motion model, especially, "Concentric7" between the connecting rod and piston pin (run across Figure S5.22b). This mate is chosen to monitor the reaction force acting on the connecting rod for structural analyses.

A motion simulation called "Motility Study" has been created. An initial athwart velocity is defined and a force is applied to the piston at the beginning of the simulation. The initial velocity of 1215 rpm is defined on the crankshaft, as shown in Figure S5.23. A forcefulness of 600 lbf is applied to the top face of the piston for a brusque elapsing of 0.002 s, corresponding to nearly six.5° of one rotation, equally shown in Effigy S5.24, to mimic the engine combustion forcefulness. Note that the strength is applied but once at the beginning of the simulation, which is certainly not realistic. The combustion force cannot be practical to every single combustion cycle accurately due to the limitations of Motion capability.

Information technology will be more than realistic if the strength can exist applied when the piston but starts moving downward (negative Y-management) and can be applied only for a selected short period. In order to do then, nosotros will have to ascertain sensors that monitor the position of the piston for the combustion load to be activated. Unfortunately, such a capability is not bachelor in Movement. Therefore, the strength is simplified as a step part of 600 lbf along the negative Y-management and practical for 0.002 s at the beginning of the simulation.

1 result plot is created, which shows the reaction strength at the upper joint of the connecting rod (Concentric7). The maximum reaction force is about −600 lbf at the beginning of the simulation. Click Results from the Motion Director window to see an existing plot (Plot2<Reaction Force2>). Right-click Plot2 and choose Edit Feature to see the plot definition (Effigy S5.25). Close the Results dialog box, correct-click Plot2<Reaction Force2>, and so cull Evidence Plot. The graph of results appears every bit in Figure S5.26a . The reaction force due to inertia can be observed by zooming in the y-centrality, in which the force reaches about 10 lbf, as shown in Figure S5.26b. For more data regarding the utilise of motion, readers are referred to Chang (2014b).

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Motion Analysis

Kuang-Hua Chang , in e-Blueprint, 2015

viii.4.1.3 Constraints

As mentioned earlier, an unconstrained rigid body in space has half dozen degrees of freedom: three translational and three rotational. When a joint (or a constraint) is added betwixt two rigid bodies, degrees of freedom between them are removed. In CAD, more commonly employed joints (e.grand., revolute, translation, cylindrical) have been replaced past assembly mates. Like joints, assembly mates remove degrees of freedom betwixt parts.

Each independent movement permitted by a constraint (either a joint or a mate) is a free degree of liberty. The free degrees of freedom that a constraint allows can exist translational or rotational along the 3 perpendicular axes. For example, a concentric mate between the propeller assembly and the instance of a single-piston engine shown in Effigy 8.thirteen allows 1 translational DOF (move along the eye axis—in this instance the Ten-axis) and one rotational DOF (rotating forth X-axis). Since the case assembly is stationary, serving as the ground body, the propeller assembly has two free DOF. Adding a coincident mate betwixt the two respective faces of the engine case and the propeller shown in Figure viii.thirteen removes the remaining translational DOF, yielding a desired associates that resembles the concrete state of affairs—that is, with only the rotational DOF (forth the X-axis).

In creating a motion model, instead of all movements being completely fixed, certain DOF (translational and/or rotational) are left to allow desired movement. Such a movement is either driven by a motor, resulting in a kinematic analysis, or determined by a force, leading to a dynamic analysis. For example, a rotary motor is created to drive the rotational DOF of the propeller in the engine example. This motor rotates the propeller at a prescribed angular velocity. In addition to a prescribed velocity, the motor may be used to drive a DOF at a prescribed displacement, either translational (using a linear motor) or rotational (using a rotary motor).

It is extremely important to understand assembly mates in social club to create successful motion models. In add-on to standard mates such every bit concentric and coincident, CAD (SolidWorks, for example) provides advanced and mechanical mates, every bit discussed in Chapter 4. Advanced mates provide additional ways to constrain or couple movements between bodies. Mechanical mates including cam-follower, gear, hinge, rack and pinion, screw, and universal joint, are essential for motion models yet extremely piece of cake to create in CAD.

In addition to mates, SolidWorks Move provides 3D contact constraint, which helps to simulate physical problems involving contacts between bodies. Substantially, 3D contact constraint applies a force to dissever the parts when they are in contact and prevent them from penetrating each other. The 3D contact constraint becomes active as before long as the parts are in contact.

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Product Data Management

Kuang-Hua Chang , in e-Design, 2015

6.v.2.ii Importing Pro/ENGINEER Assembly to SolidWorks

We import the input gear assembly shown in Figure 6.17(a) using both options. As shown in the left of Figure half-dozen.17(a) (Pro/ENGINEER model tree), there are xi parts in this associates.

Using the option of importing solid features, parts are not completely imported, as shown in Figure 6.17(b). Major solid features are missing, such as pinion ane (wheel_gbox_pinion_1s<one>), where most solid features are non imported. In fact, there are only two extrude features successfully imported. The remaining entities are by and large sketches. Some parts seem to exist imported fine. Nonetheless, the Mates co-operative in the browser is completely empty, implying that no associates mates have been imported.

Apparently, this translation is not satisfactory. A nontrivial effort volition have to be devoted to reconstructing the solid features (therefore, solid models) equally well as the final assembly.

The option of importing geometry is as well more than straightforward for assembly. In fact, the assembly and all 11 parts seem to be correctly imported, as shown in Effigy half-dozen.17(c). By expanding any of the parts listed in the browser, such as the gear (wheel_gbox_pinion_1s<1>), we run across an imported feature listed, as depicted in Figure 6.17(c). Once again, at that place is no solid feature converted in any of the parts. In addition, the Mates branch is empty.

If we do not anticipate making any change to this input gear assembly, this imported associates is satisfactory, except it does non take any assembly mates. Associates of all 11 parts (maybe more, for other cases) will exist a nontrivial endeavor. If you practise not anticipate making changes in how these parts are assembled, you may merge all eleven parts into a single part, instead of assembling those using mating constraints.

A stride-by-stride detail of importing the Pro/ENGINEER part and assembly can exist found in the tutorial lesson S1.iii. You may go over the lesson to learn more about the model importing capabilities offered by SolidWorks.

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Assembly Modeling

Kuang-Hua Chang , in due east-Design, 2015

4.2.ane Mating Constraints

There are six DOFs for each component in infinite: three translations and three rotations. In the geometry mating approach, users specify the relative positions of parts by interactively defining spatial relationships between the geometric elements of mating parts. The geometric elements used in geometry mating include points, planar faces, surfaces, and axes of cylinders and holes. Usually employed mating constraints (or placement constraints in Pro/ENGINEER and associates mates in SolidWorks) include coincident-mate, mate first, coincident-aligned, concentric (or fit), angle, parallel, and align. These mating constraints are usually practical to the aforementioned type of geometric entities, such as a pair of planar faces for a coincident-mate, or different entities, such as a point on a bend for a path mate.

In CAD, the first part brought into the assembly is fixed to the default datum features with all half-dozen DOFs constrained. In Pro/ENGINEER, the first part tin be assembled to the assembly datum features, such every bit datum planes or the datum coordinate arrangement, using placement constraints (e.chiliad., by adjustment their corresponding coordinates). In SolidWorks, the first component is stock-still past aligning the component coordinate system with the default coordinate system provided in the assembly (also called the world coordinate organization or WCS). The first part serves as the base part for assembling other parts. When an existing part is brought into the associates, there are an additional six DOFs associated with it for the designer to work with.

Most mating constraints restrict part movement between regular surfaces, such as apartment surfaces and cylindrical surfaces. As a consequence, a mating role is allowed to translate or rotate forth a fixed direction if it is underconstrained. For example, the lower shaft of the creepo is to be inserted into the hole of the bearing, as shown in Effigy 4.iii. The bearing is fixed. The crank is assembled to the begetting using 2 mating constraints, concentric (called Mate: Concentric in SolidWorks and Insert in Pro/ENGINEER) and coincident-mate (called Mate: Coincident in SolidWorks and Mate or Align Surfaces in Pro/ENGINEER). The concentric mating constraint eliminates ii translational DOFs and two rotational DOFs. The coincident-mate mating constraint eliminates one translational DOF and ii rotational DOFs. As a effect, simply i DOF, Rz, remains, as summarized in Table 4.1. SolidWorks allows designers to motility (rotate) the crank by simply dragging the function, according to the costless DOF. The designer is able to check the kinematics of the product in the assembly mode. In Pro/ENGINEER, such a rotational DOF is allowed to be undefined; similarly in SolidWorks, components can exist dragged to bank check the kinematic beliefs of the assembly.

Table 4.1. Degrees of Liberty Eliminated past the Two Mating Constraints in Figure four.iii

	T 10	T y	T z	R x	R y	R z
Mate: Concentric	×	×		×	×
Mate: Coincident			×	×	×

Note that in Figure 4.3(b), the coincident-mate mating constraint is more precisely called coincident with antialigned condition. In SolidWorks, you lot tin can set the alignment condition. The alignment conditions for a coincident mating constraint are either aligned, in which vectors normal to the selected faces bespeak in the same management; or antialigned, in which vectors normal to the selected faces point in contrary directions, as illustrated in Figure four.4(a). For cylindrical surfaces, the axis vector is aligned or antialigned, as illustrated in Figure four.4(b).

The most normally used mating constraints in Pro/ENGINEER and SolidWorks are listed in Table four.2. In add-on, a complete list of standard mating constraints in SolidWorks with mate symbols is provided in Table 4.3. Yous may expect to utilize these mating constraints to create an associates in SolidWorks and near modern CAD systems. In SolidWorks, mating constraints (standard) are imposed to surfaces, which are physically intuitive. In Pro/ENGINEER, in improver to surfaces, some mating constraints are applied to abstract geometric entities, such as betoken-on-surface and edge-on-surface constraints. In some cases, Pro/ENGINEER and SolidWorks will non accept the mate constraints as defined if they conflict with existing ones.

Table four.two. Mating Constraints in Pro/ENGINEER and SolidWorks

Pro/ENGINEER	SolidWorks	Descriptions
Mate surfaces	Mate: Coincident, antialigned	Positions selected faces or planes so they coincide. Antialigned implies that the 2 faces or planes mate and the normal vectors of the two faces or planes point in the opposite directions, and aligned implies that the normal vectors of the two faces or planes betoken in the same directions
Align surfaces	Mate: Ancillary, aligned
Marshal axes or insert surfaces	Mate: Concentric	Places the selected cylindrical surfaces so that they share the common axis
Orient	Mate: Parallel	Places the selected items so they prevarication in the same direction and remain a constant altitude autonomously from each other
Coordinate system	Default	Identify the starting time office to the default coordinate organisation in assembly
Tangent	Mate: Tangent	Places the selected items in a tangent mate (at least i item must be a cylindrical surface)

Tabular array 4.3. Standard Mates in SolidWorks

Standard Mates	Descriptions from SolidWorks Aid
Ancillary	Positions selected faces, edges, and planes (in combination with each other or combined with a single vertex) so they share the same space plane. Positions ii vertices so they touch
Parallel	Places the selected items so they remain a constant altitude apart from each other
Perpendicular	Places the selected items at a 90° angle to each other
Tangent	Places the selected items tangent to each other (at to the lowest degree 1 selection must be a cylindrical, conical, or spherical face)
Concentric	Places the selections so that they share the same center line
Lock	Maintains the location and orientation between two components
Distance	Places the selected items with the specified distance between them
Bending	Places the selected items at a specified angle to each other
Default	Places the first part to the default coordinate organisation in assembly

In this chapter, we adopt SolidWorks terminologies for mating constraints, except that we use coincident-mate instead of ancillary antialigned.

In addition to standard mates, such as concentric and coincident, some CAD systems, such as SolidWorks, offer advanced mates, as listed in Table 4.4. Advanced mates provide additional ways to constrain or couple movements between parts. A coupler removes one boosted degree of freedom from the kinematic model. For example, a linear coupler shown in Figure 4.5(a) removes one translational DOF by coupling the corresponding translational DOF between components i and 2. Also, path mate (one of the advanced mates in SolidWorks) allows a part to move along a curve slot, a groove, or fluting, varying its moving direction specified by the path bend. For example, in the rail and carriage assembly of the send device shown in Figures four.one and 4.2, a vertex in the carriage is moving forth the sweep curve (which can be either open- or closed-loop, composed of several curves) of the track, equally shown in Figure 4.5(b). Every bit a result, path mate allows the carriage to move along the bend groove of the rail, varying its moving management specified by the path curve. In addition, the pitch, yaw, and roll of the moving part tin be defined to resemble the physical conditions. Such a capability supports animation and kinematic analysis for a whole new set of applications that involves curvilinear motion.

Table 4.four. Advanced Mates in SolidWorks

Advanced Mates	Descriptions
Symmetric	Forces two similar entities to be symmetric about a plane or planar face
Width	Centers a tab within the width of a groove
Path	Constrains a selected signal on a component to a path
Linear/Linear coupler	Establishes a relationship betwixt the translation of one component and the translation of some other component
Limit	Allows components to motion within a range of values for altitude and angle mates

Some CAD systems, such as SolidWorks and Pro/ENGINEER, likewise offering mechanical mates, such as cam follower, gear, hinge, rack and pinion, screw, and universal joint. These are essential for kinematic analysis of the production design. More about kinematic and dynamic analysis can exist found in Chapter 8 Movement Analysis. Tutorial lessons can exist plant in Projects P2 and S2 for Pro/ENGINEER and SolidWorks, respectively. More than tutorial lessons tin likewise be found in Chang (2010).

Next, we utilise a slider-crank case shown in Figure four.6 to illustrate the mating constraints employed for the assembly in SolidWorks. We will use the same example in Department 4.2.ii to illustrate the joint constraint approach for associates as in, for instance, Pro/ENGINEER. Notation that model files of both examples are available for download at the book's companion website http://booksite.elsevier.com/9780123820389.

The slider-crank mechanism consists of five parts and one subassembly. They are begetting, crank, rod, pivot, piston, and rod subassembly (consisting of rod and pin rigidly connected). An exploded view of the mechanism is shown in Figure iv.6(b). There are eight assembly mates, including five ancillary and three concentric, defined in the assembly.

The showtime three mates (Concentric1, Coincident1, and Coincident2) assemble the crank to the fixed bearing, every bit shown in Effigy 4.7(a). Every bit a result, the crank is completely fixed. Note that the mate Coincident2 orients the creepo to the upright position, defining the configuration of the mechanism. Suppressing this mate will allow the creepo to rotate with respect to the bearing.

The next two mates (Concentric2 and Coincident3) gather the rod to the crank, as shown in Figure 4.7(b). Unlike the crank, the rod is allowed to rotate with respect to the crank. The adjacent two mates (Concentric3 and Coincident4) gather the piston to the pin, allowing the piston to rotate most the pin. The final mate (Coincident5) eliminates the rotation by aligning two planes, Plane3 of the piston and the Plane2 of the bearing, every bit shown in Figure 4.7(c).

At this point, the entire assembly is fully constrained. No relative motion between whatsoever components is allowed. If we suppress Coincident2 divers betwixt the right aeroplane of crank and right plane of the bearing, the crank is allowed to rotate along the z-management of the WCS. If you lot elevate the crank (or any component), the unabridged assembly is moving, as illustrated in Figure 4.8.

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Small Form Factor Fiber Optic Connectors

John Fox , Casimer DeCusatis , in Fiber Optic Data Communication, 2002

3.4. VF-45 Connector

The VF-45 connector, developed by 3M, is possibly the nigh innovative SFF connector design, in that it eliminates the need for precision ferrules and sleeves birthday. The overall look and experience of the "Plug-to-socket" design closely resembles the standard telephony RJ-45 "Connector-to-jack" system whereby the cable assembly mates straight to a terminated socket, reducing the need for couplers ( Fig. 3.nine). Although this concept has been effectually for years in the copper industry, the creation of a bare fiber optical interface, using alignment grooves and no index matching gels, requires some revolutionary techniques.

The VF-45 connector incorporates two 125-um optical fibers, suspended in free space on a four.v-mm pitch protected by a RJ-45 style housing with a retractable front door designed to protect the fibers. The connector design supports both unmarried-mode and multimode tolerances by relying on the inherent precision of the optical fibers within the two injected molded v-grooves of either the transceiver or a VF-45 socket. The blueprint of the interconnect allows the natural bound forces of the optical fibers to align the fibers within the v-grooves besides equally ensuring physical fiber-to-fiber contact.

Because of the uniqueness of this interconnect the geometry of the endface polish of both the plug and receptacle fibers has been modified to provide optimum performance. The VF-45 optical connection relies on the leap force created by the bowing of the optical fibers to provide a physical contact force of approximately 0.1 N and this force coupled with an viii-degree bending polished endfaces produces the optimum connection and render loss results. The tips of the plug fibers are also askew at 35 degrees, allowing a 90-um contact area and providing a relief for the fiber to slide into the v-grooves with no impairment to the core region (Fig. 3.ten). This chamfer is not required on the receptacle fibers since they remain stationary while the plug fibers may have to endure multiple insertions (Fig. three.eleven). Every bit previously mentioned, the contact force created at the optical interface directly influences the optical performance of the plug-socket connection. This downward compressive force is generated when the two fibers of the plug appoint with the resident fibers of the socket and cause a slight "bow" in the plug fibers (Fig. 3.12). Because of the constant stress on these fibers, long-term reliability on standard optical fibers became a concern and therefore a specialized loftier-forcefulness optical fiber was developed for this application, called GGP (glass-glass-polymer) fiber. GGP cobweb consists of 100-um glass cobweb with a polymeric coating applied to bring the outer bore to 125 um. By reducing the outer diameter of the glass the tensile stress on the cobweb is minimized and the additional blanket likewise provides protection against abrasions from the v-grooves and reduces the chance of harm to the glass during the mechanical stripping procedure used in the termination process.

The manufactory termination of the VF-45 jumper plugs is considerably different than the conventional ferrule-based connectors. The process of threading a 125-um fiber into a precision ferrule hole filled with epoxy is now eliminated and replaced with a mechanical cobweb holder that grips the fibers in place. The fibers are then cleaved and polished to the endface geometry previously described and the cable strain relief slid into place. The fibers and holder are then placed into a protective shroud and the forepart door cover installed. The relative simplicity of this manufacturing process makes the VF-45 connector one of the best candidates for a fully automated production line.

The socket of the VF-45 was specifically designed for termination in the field with minimal effort and training. Afterward preparing the fibers for termination by removing outer buffer material, they are inserted into a mechanical cobweb holder that retains the fiber by gripping them inside a deformable aluminum crimp. The fibers are then cleaved and manus-polished to an eight-degree angle with a slight radius generated by the durometer of the polishing pad. The fiber holder with the polished fibers is guided into the socket 5-grooves and the housing plate snapped into place (Fig. 3.13). Although this method of field termination does vary from the other pre-polished SFF connectors, the total termination time and the complication of the process is very similar.

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The Dynamic Simulation Surroundings

Wasim Younis , in Up and Running with Autodesk Inventor Simulation 2011 (2nd Edition), 2010

Redundant joints

Back-up, or redundant joints, occurs when an assembly or mechanism is overconstrained as a outcome of applying joints. This makes the assembly statically indeterminate, which means the associates has infinite solutions for joint types and thus reaction forces. In order to explain this concept of redundancy, we will use the following door assembly, comprising a door and a frame. Most residential doors have at least two hinges, and some loftier-security doors will take three hinges, if not more than.

The door example has two components, a frame and a door. Each unconstrained component has six degrees of freedom, and by applying joints we restrict motion by restricting these degrees of freedom. In nearly door frame examples, the frame is, normally, completely stock-still to walls, therefore restricting all degrees of freedom. The equivalent to this in Inventor and Simulation is to ground the component. The door, however, is fixed to the frame by a serial of hinges, which restrict the motility of the door to one rotational degree of freedom to enable the door to open and close. The equivalent joint to this hinge activeness is the revolution joint, as illustrated below.

With this in heed, we will attempt to ground the frame and apply a revolution joint at each hinge position between the door and frame. Initially, we will apply ii revolution joints in the following example.

1.: Open doorframe.iam

Six constraints take been created, resulting in overconstraining. This is so that you will not need to create any more constraints for this do.

The frame is prepare to ground as a result of information technology being the first part to exist placed in the assembly; hence, at that place is no need to ground it once again. Farther, each hinge location has the following ii assembly mate constraints:

▪: Edge-edge constraint
▪: Indicate-bespeak constraint
2.: Select Environments tab > Dynamic Simulation

In the Dynamic Simulation browser, all components are grounded. At this stage, we tin can either create joints automatically or convert assembly constraints; obviously, the former is quicker, and then nosotros will try that commencement.

3.: Select Simulation Settings
4.: Inside the Dynamic Simulation Settings dialog box, select Automatically Convert Constraints to Standard Joints > Click OK

A welding joint has been created as a result of overconstrained assembly constraints (six in full; a maximum of three is normal). As this joint has welded the components together such that there is no relative move between the components, we need to switch off the automatic conversion of joints and create joints manually from Convert Associates Constraints.

5.: Select Simulation Settings and clear Automatically Convert Constraints to Standard Joints > Click OK

No joints will now be created, every bit shown here.

6.: Select Convert Constraints
vii.: Select the door and frame when the Convert Assembly Constraints dialog box appears

In the Catechumen Associates Constraints dialog box, all constraints betwixt the two components will exist selected and no joints will be translated. In addition, the following alarm will appear, as six constraints have been practical between the 2 components.

9.: Click OK to accept the alert
10.: Deselect all constraints apart from those of Top-hinge:ane and :ii, as shown > Click OK to any warning that appears when deselecting constraints

11.: Click OK

As a upshot of selecting the edge-border and signal-bespeak constraint, Dynamic Simulation has created a revolution joint, equally expected.

Now, nosotros need to create a revolution joint at the bottom hinge.

12.: Repeat Steps 6–9 and select the following constraints:

13.: Click OK > Accept the following warning:

Past accepting the alert, we have created a redundant joint, as illustrated below:

So, the question is, why accept we got a redundant joint as well-nigh doors have two hinges (i.due east. two revolution joints)? Let's examine the table below.

Based on the above table, the door only seems to need one revolution joint to work properly every bit the resultant caste of freedom is 1, which allows the door to open and close.

Dynamic Simulation cannot simulate deformity in components when the force causing the deformity is large plenty; further, the joints created are perfect in that they practice not allow for manufacturing tolerances/imperfections and clearances. For these reasons, the second joint created becomes redundant, and the reaction forces produced will not be unique and, more importantly, can be unpredictable if redundancy in the model is not removed. Apart from the forces, all results are unique and are totally anticipated.

At this stage, we have 3 options.

Option ane – Simulate the door and frame using one revolution joint.

▪

Reward – Will not create a redundant model and the results will exist unique.

▪

Disadvantage – This method will create unnecessary moments that would non occur with 2 revolution joints.

Option 2 – Simulate the door and frame using two revolution joints.

▪

Advantages

□: Will produce equal reactions between both joints.
□: Will not induce unnecessary moments as a result of having one joint.

▪

Disadvantage – This method volition create a redundant model.

Choice 3 – Simulate the door and frame using 2 joints that practice non result in a redundant model.

▪

Advantage – Volition not create a redundant model and the results volition be unique.

▪

Disadvantage – The success of this model relies on the direction of the loading. This will be explained later.

To get through each of the above options, we volition determine the reactions at each articulation as a result of gravity and the mass of the door.

As we accept already created the 2 revolution joints (Pick 2), we will determine the reactions and moments of these joints commencement.

14.: Play Simulation > Select Output Grapher

15.: Select Forcefulness for both joints to brandish the reaction forces at the swivel due to the mass of the door and gravity

Despite the fact that the model is redundant, the reaction forces are right, as nosotros would await l% of the weight to be distributed through each hinge.

The mass of the door is 69 kg.

The gravity is 9.81 one thousand/s².

Therefore, weight of door = 69 × 9.81 = 676.89 Northward.

Half of this is 338 N.

16.: Minimize the Output Grapher
17.: Select Structure Mode

18.: Now delete both revolution joints (Pick i)

Now, we volition create a nonredundant model by creating one revolution joint.

19.: Select Catechumen Constraints to create a single revolution articulation in the middle hinge

You may demand to Click OK to the warning messages several times .

xx.: Click OK. The post-obit joint will be created:

21.: Play Simulation > Maximize the Output Grapher

Despite simply using one revolution joint, the maximum reaction value is correct at 677 North. Even though the solution does non create any redundancies, it does not stand for reality accurately as all doors have at to the lowest degree 2 hinges or joints. It may too create boosted moments that may not otherwise be present.

22.: Minimize Output Grapher > Select Construction Mode
23.: At present delete the single revolution articulation

Now, we volition create a third option by creating i spherical and ane signal-line articulation.

24.: Select Convert Constraints
25.: Select the door and the frame and for the top swivel select the constraint shown below, and then click Use

You may need to click OK to the alert messages several times.

26.: Select the door and the frame and for the lesser hinge select the constraint shown below > Click OK

You may need to click OK to the alarm letters several times.

27.: Accept the warning

As a issue of accepting the warning, we accept a redundant model overconstrained past one degree of freedom.

28.: Right click Lesser-hinge:ii > Select Edit
29.: Reselect Component 2 of the constraint and pick the edge as shown > Click OK

30.: Have the warning > Click OK

The joint changes to indicate-line and the model has no redundancies.

31.: Play the simulation
32.: Maximize the Output Grapher and select the forces to brandish the results

The results are non what we expected as they are not symmetrically distributed through each joint. The reason for this is that the top spherical joint has taken well-nigh of the reaction and the lower joint has taken much less. This is because the point-line constraint does not restrict motion in line with the gravity, as it is free to move in that direction. And then, even though the model is nonredundant, the values are not equal. Let's endeavour changing the position of the gravity.

33.: Minimize Output Grapher > Select Construction Mode
34.: Right click Gravity > Select Define gravity
35.: Change the position of the gravity equally shown:

36.: Click OK > Play the simulation
37.: Maximize the Output Grapher
38.: Close door frame.iam

The results are now more than reasonable. These results are meliorate than the previous ones considering gravity is not in line with the direction of the point-line axial move. So, keep this in mind when creating nonredundant models/joints.

In Summary

Option i – If the ultimate goal of the simulation is to determine the effects of inertia and dynamics, Solution 1 will suffice.

Option 2 – If the ultimate goal of the simulation is to perform a stress assay on the door and you desire to make use of the load transfer facility, Solution ii is the most advisable equally it provides even reactions at the joints. In reality, we always use equal strength hinges as we always assume even load distribution.

Option 3 – Is likewise acceptable, provided the loading is non in the direction of the point-line axial motility.

Pick 3 will not work for a iii-hinge door.

Information technology is not advisable to use redundant constraints; all the same, if they are employed, use them with caution as the forces produced will not be unique or even worst case.

Suggested Workflow to Avert Redundant Joints

Using Automatically Convert Constraints to Standard Joints later on creating all the constraints is non advisable, especially for a big assembly, as it can become slow to remove redundancies past altering assembly constraints, every bit this is the simply mode to modify joints. With this in view, the following ii approaches are suggested.

Option 1 – Automatic joints

As you tin can create associates constraints within the Simulation environment, it is advisable to outset (or continue) the constraining process within the Simulation environment. The main benefit of this is that, with Automatically Convert Constraints to Standard Joints activated, you lot will see the blazon of joint created as soon as you identify the constraints. This way, information technology is easier to manage and fix redundant joints as they appear during the constraining process.

Option 2 – Transmission joints

Creating standard joints manually inside the Simulation environment will provide more than control in removing redundancies from within the model. However, this selection tin can be slow and tedious.

The process of Selection 2 tin be enhanced by additionally using the Manually Convert Constraints feature for some joints.

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montoyaplesubt.blogspot.com

Source: https://www.sciencedirect.com/topics/engineering/assembly-mate

what type of mate would you use to align a rod in a hole?

Design with SolidWorks

S5.3.i.1 Motility model and simulation

Motion Analysis

viii.4.1.3 Constraints

Product Data Management

6.v.2.ii Importing Pro/ENGINEER Assembly to SolidWorks

Assembly Modeling

4.2.ane Mating Constraints

Small Form Factor Fiber Optic Connectors

3.4. VF-45 Connector

The Dynamic Simulation Surroundings

Redundant joints

In Summary

Suggested Workflow to Avert Redundant Joints

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